JP2022533946A - Spool valve used in variable vane pump - Google Patents

Abstract

A variable displacement vane pump is disclosed. The pump includes a control chamber located between a housing and a control slide. A pressure control relief valve is in fluid communication with the discharge passage and moves to close or open the relief port based on the output pressure of the lubricant. A feedback channel fluidly connects the control chamber to the suction path of the pump. This feedback channel also connects to a control port that is connected to the main control valve. The relief valve and control valve are separate and not fluidly connected. When the pressure in the discharge path exceeds a predetermined amount, movement of the relief valve opens the relief port and delivers a portion of the output lubricant through the relief port to the control chamber. This pressurizes the control chamber and reduces the eccentricity of the pump by displacing the control slide.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS This application claims priority to U.S. Provisional Patent Application No. 62/850,074, filed May 20, 2019, the entire contents of which are incorporated herein by reference. incorporated into the book.

The present disclosure relates generally to variable displacement vane pumps for supplying pressurized lubricating oil to a system. More specifically, the present disclosure relates to integrating a fail-safe feature into the pump in the form of a pressure control relief valve that is connected to the outlet space and controlled to reduce eccentricity. Provide feedback to the chamber.

Vane pumps are known for use in pumping fluids such as oil or lubricants into internal combustion engines. A known system is known that utilizes a single control chamber to move the lubricant. Examples of passively controlled variable vane pumps with one control chamber are described in US Pat. No. 2003/0120002, the entire contents of which are incorporated herein by reference. Other types of pumps are disclosed in U.S. Pat. Nos. 8,047,822, 8,057,201 and 8,444,395, also incorporated herein by reference in their entireties. be done.

U.S. Pat. Nos. 9,534,519 and 10,030,656, the entire contents of which are incorporated herein by reference, describe motorized valves (e.g., PWM (Pulse Width Modulation) valves) in addition to control valves. An example of a vane pump that utilizes is described. The '519 and '656 patents communicate through a motorized valve to control the supply to and from the control chamber, providing a fail-safe function when the motorized valve becomes disabled or fails. can be executed. Additionally, the '519 and '656 patents block the vent port/channel for the control chamber before outlet pressure is applied to the control chamber.

One aspect of the present disclosure provides a variable displacement vane pump for injecting lubricant into a system. The pump includes a housing having an inner surface defining an inner chamber, an inlet for injecting and pressurizing the lubricating oil into the housing, the inlet being connected to an inlet path in the housing, and an inlet. a discharge port for delivering pressure lubricating oil from the housing to the system, the discharge port being connected to a discharge passage provided in the housing. The pump also includes a control slide displaceable about a pivot pin within the interior chamber of the housing, the control slide having (a) an increasing displacement direction for increasing pump displacement; a control slide displaceable in a displacement decreasing direction to reduce pump displacement, said control slide having an inner surface defining a rotor receiving space; mounted in said rotor receiving space of said control slide; a rotor having at least one vane, the rotor rotating within and relative to the control slide about an axis of rotation to pressurize the lubricating oil injected through the suction passage; and wherein said at least one vane is configured to engage said inner surface of said control slide when rotating. The suction port and the discharge port are arranged on opposite radial sides of the rotation axis of the rotor. The inlet is provided on a first radial side and the outlet is provided on a second radial side opposite to the first radial side. The elastic member urges the control slide in the discharge amount increasing direction. The resilient member is provided on the first radial side of the rotor and the pivot pin is provided on the second radial side of the rotor. The pump includes a control chamber for receiving pressurized fluid provided between the housing and the control slide, the pressurized fluid being configured and arranged to move the control slide in the decreasing discharge direction. placed. The control chamber extends on both the first radial side and the second radial side of the rotor. A relief port is provided in the housing for selectively communicating fluid from the discharge passage to the control chamber. A feedback channel is provided within the housing and fluidly connects to a control port, which is connected to a main control valve configured to control pressure within the control chamber. A pressure control relief valve is provided within the housing, the relief valve having an actuating surface in fluid communication with the discharge passage and responsive to a predetermined pressure of the lubricating oil acting on the actuating surface. based on the first valve position to the second valve position. The main control valve is configured to control the pressure in the control chamber independently of the position of the relief valve, the control for displacing the control slide in the direction of decreasing delivery. delivering pressurized lubricant to pressurize the control chamber; and discharging pressurized lubricant from the control chamber to permit displacement of the control slide in the increasing displacement direction. In the first valve position, the relief valve is inactive, blocking fluid communication from the discharge passage through the relief port to the control chamber. In the second valve position, the relief valve permits fluid communication of the lubricant from the discharge passage through the relief port to the control chamber, thereby pressurizing the control chamber and controlling the main control. The control slide is displaced in the discharge rate decreasing direction independently of the valve.

Another aspect provides a system comprising a variable vane pump as described above, an engine, and a lubricating oil sump containing lubricating oil, wherein said pump delivers said lubricating oil to said engine.

Yet another aspect provides a method of reducing the amount of eccentricity in a variable vane pump as described above. The method comprises the steps of hydraulically moving the pressure control relief valve from the first valve position to the second valve position based on the predetermined pressure of the lubricating oil acting on the working surface; permitting fluid communication of the lubricating oil from a discharge passage through the relief port to the control chamber, thereby pressurizing the control chamber to cause the control slide to reduce the discharge independently of the main control valve; and displacing in a direction. The main control valve is configured to control the pressure in the control chamber independently of the position of the relief valve, the control for displacing the control slide in the direction of decreasing delivery. delivering pressurized lubricant to pressurize the control chamber; and discharging pressurized lubricant from the control chamber to permit displacement of the control slide in the increasing displacement direction.

Other features and advantages of the present invention will become apparent from the following detailed description, the accompanying drawings and the appended claims.

1 is an overhead or top view of a pump and housing according to an embodiment of the present disclosure with its cover removed and the control slide in the first position; FIG.

Figure 2 is an alternative top view of the pump and housing of Figure 1 with the cover removed and the control slide in the second position;

Figure 3 is a side view of the pump and housing shown in Figures 1-2, including a cover and drive, according to an embodiment;

FIG. 4 is a cross-sectional view along line AA of FIG. 3 showing part of the inlet and outlet ports and the location of the relief valve within the housing of the pump;

FIG. 4B is an alternative cross-sectional view of the relief valve of the pump, showing further details of the relief valve;

2 is a cross-sectional view along line BB of FIG. 1 showing the relief valve in a closed position according to an embodiment; FIG.

FIG. 7 is a perspective view of the cross section of FIG. 6 viewed obliquely;

2 is a cross-sectional view along line BB of FIG. 1 showing the relief valve in an open position according to an embodiment; FIG.

FIG. 9 is a perspective view of the cross section of FIG. 8 as seen from an oblique direction;

1 is a schematic diagram of a system according to an embodiment of the present disclosure; FIG.

The description set forth below with reference to the accompanying drawings is intended to describe various embodiments of the disclosed subject matter, and is not necessarily intended to be representative only of the following embodiments. By way of example, the following description sets forth specific details for the purpose of providing a better understanding of the disclosed embodiments. However, it will be apparent to one skilled in the art that the disclosed embodiments may be practiced without these specific details. In other instances, well-known structures and components are shown in block diagram form in order to avoid obscuring the disclosed subject matter.

When referred to herein as "an embodiment" or "an embodiment," the particular feature, structure or property described in connection with that embodiment is included in at least one embodiment of the disclosed subject matter means that Thus, various references to "in one embodiment" or "in an embodiment" throughout this specification are not necessarily all referring to the same embodiment. Moreover, such specific features, structures or characteristics may be combined in any suitable manner in one or more embodiments. Also, the disclosed subject matter embodiments are intended to encompass variations and modifications.

Terms such as "upper", "lower", "lateral", "upper", "lower", "inner", "outer", "inner", "outer", etc., when used herein refer only to It should be understood that this reference is made for purposes only and does not necessarily limit the embodiments of the present disclosure to any particular orientation or configuration. Moreover, terms such as “first,” “second,” etc. simply identify one of the plurality of parts, components, steps, operations, functions and/or points of reference disclosed herein. and does not necessarily limit the embodiments of the present disclosure to any particular configuration or orientation, or to the requirements of each number.

As will be described in detail below, the variable displacement vane pump has a control slide displaceable within a housing and at least one control chamber within the housing that receives pressurized lubricating oil. The housing of the pump also includes a vent or feedback channel for supplying a portion of the lubricating oil to the control chamber and exhausting it from the control chamber to the main control valve. Additionally, pressure control valves (e.g., spool valves, relief valves, directional control valves, pilot valves, or more simply control valves) may serve as fail-safe or safety features for regulating pump displacement. , are provided in the housing of the pump of the invention. A pressure control valve (referred to in this disclosure as a "relief valve" and/or a "spool valve") is configured to open a first a hydraulically actuated valve movable from a valve position of 1 to a second valve position. Specifically, the valve of the present invention includes a sliding spool whose position relative to the casing or housing restricts or permits flow through the relief port of the pump housing, thus restricting fluid flow within the pump. can help control. In one embodiment, the control valve actuates to the second valve position when the pressure of the pressurized lubricant exceeds a threshold value (e.g., above the desired pressure), thereby providing relief from the discharge path. Allow fluid communication to the control chamber through the port. This allows the control chamber of the pump to be pressurized independently of the main control valve to displace the control slide in the direction of decreasing displacement, thereby reducing the eccentricity of the pump.

Those skilled in the art will appreciate that the terms "pump capacity" or "displacement" as used in this disclosure refer to the volume of fluid (lubricant) that a pump can move in a specified period of time, i.e., the flow rate can be understood to mean In accordance with the present disclosure, references to a fluid/lubricant/oil having a (lower) or cooler temperature refer to fluid/lubricant/oil at cold start, e.g. pumps and/or systems (e.g., engine) not running. refers to the fluid/lubricant/oil when starting the Fluid/lubricant/oil temperature at cold start may vary, for example, depending on the type of fluid/lubricant/oil utilized, air temperature, and/or pump/engine idle time (when fluid/lubricant is pump/engine (including when completely discharged from the In some cases, as described below, the temperature of the fluid/lubricant/oil during a cold start can delay normal operation of the pump for a period of time. The pump features and apparatus disclosed herein may be utilized during cold start, according to some embodiments.

1 and 2 are top or overhead views of a pump 10 according to one embodiment of the present disclosure, shown with the cover removed. Pump 10 is, according to one embodiment, a variable displacement vane pump for delivering fluid or lubricant to the system. Pump 10 comprises a housing 20 having an inlet 30 and an outlet 40 . From source 26 (see FIG. 10) through inlet 30 into housing 20 flows pressurized or pumped fluid or injects lubricating oil (typically oil in the automotive field) in which lubrication is performed. Oil is pressurized. Discharge port 40 directs pressurized fluid or lubricant from housing 20 and a lubricating oil sump (shown in FIG. 10) to system 32, such as an engine or transmission (shown in FIG. 10). , used to spit or deliver. Also, as known in the art, control slide 12 (described in detail below), rotor 15, drive shaft 16, and resilient member 24 (shown in FIG. 2, additional features of the pump are more apparent). 1) is provided within the housing 20. As shown in FIG. The pump shown in FIG. 1 has a control chamber 36 (described below) which is provided between the housing 20 and the control slide 12 and receives pressurized lubricating oil to move the control slide 12 from an increasing displacement direction. A resilient member 24 biases the control slide 12 in one direction.

The suction port 30 and the discharge port 40 are arranged on opposite sides in the radial direction of the rotating shaft of the rotor 15 . As shown in FIGS. 1 and 2, for example, the inlet 30 is provided on the first radial side, i.e. the right side in these figures, and the outlet 40 is provided on the side opposite the first radial side. It is provided on the second radial side, ie the left side in these figures. The dashed lines RR shown in these figures represent the radial lines that define each radial side of the housing 20 .

Housing 20 defines at least one inlet opening 72 defining an inlet 30 for intake of fluid to be pumped, and at least one outlet opening 74 defining an outlet 30 for discharging fluid. (see FIGS. 2-4). Housing 20 also has at least one inlet port 31 defining an inlet 30 for intake of fluid to be pumped, and at least one outlet port 33 defining an outlet 30 for discharging fluid. The intake port 31 and the discharge port 33 each have a crescent shape and may be formed through the same wall located on one or both axial sides of the housing (with respect to the axis of rotation of the rotor 15). In addition, the suction port 31 and the discharge port 33 may be arranged on opposite sides of the rotating shaft of the rotor 15 in the radial direction. Such a structure has existed conventionally and will not be described in detail. Also, the shape of the suction port 30 and/or the discharge port 40 is not limited to those shown here. Other configurations may be used, such as different shapes or numbers of ports. Further, it should be appreciated that multiple inlets or outlets may be provided (eg, via multiple ports).

1 and 2, inlet 30 and inlet port 31 may be connected to an inlet passage 39 (shown radially to the right in these figures) provided in housing 20, and outlet 30 and Discharge port 33 may be connected to a discharge passage 49 provided in housing 20 (shown radially to the left in these figures). In one embodiment, the inlet channel 39 is provided adjacent the resilient member 24 and the outlet channel 49 is provided adjacent the pivot pin 28 of the control slide 12 . The suction port 31 may form part of the suction passage 39 and the discharge port 33 may form part of the discharge passage 49 .

Housing 20 may be constructed of any material and may be formed using aluminum die casting, iron sand casting, powder metal casting, forging, or any other manufacturing technique. Housing 20 encloses internal chambers including control chamber 36 (described below). In the figure, the main shell structure of the housing 20 is shown. The walls define axial sides of the inner chamber, and a peripheral wall 23 having an inner surface extends generally circumferentially to define and surround the inner chamber. A cover 21 (e.g., partially shown in FIG. 3) is provided along or around housing 20 (e.g., around or outside rotor receiving space 35) through various fastener holes 29 (FIGS. 1 and 3). It is attached to housing 20 by fasteners 27 (e.g., a side view of some fasteners are shown in FIG. 3) (e.g., bolts) that are inserted into housing 20 (as shown in FIG. 3). For example, Figures 1 and 2 do not show the cover, but show some of the internal components of the pump. However, the use of such covers is common practice and will not be described in detail below. The cover may be constructed of any material and formed using stamping (e.g., steel or other metal stamping), aluminum die casting, iron sand casting, powder metal casting, forging, or any other manufacturing technique. you can Also shown are the housing 20 as well as the underside and portions of the cover surrounding the internal chamber of the pump 10 . A gasket or other sealing member may optionally be provided between the cover and the peripheral wall of housing 20 to seal the interior chamber. Additional fastener holes for receiving fasteners may be provided along the peripheral wall of pump 10 to secure pump 10 to, for example, an engine.

The housing 20 and cover have various surfaces for accommodating movement and sealing engagement of the control slide 12 . This will be described in detail later.

A control slide 12 (also known in the art as a "control ring") is positioned relative to the cover within housing 20 between at least a first and a second sliding position (or intermediate positions between the two). , and depending on the case, the third slide position), thereby adjusting the discharge rate of the pump 10 from the discharge port 40 (for example, the discharge rate from the discharge port 33), ie, the flow rate. In one embodiment, control slide 12 is pivotally mounted and configured to rotate within housing 20 between a first slide position and a second slide position. For example, the control slide 12 can be pivoted with respect to the inner chamber. If the control slide 12 is displaced away from the first slide position, it is considered to be in the second slide position regardless of the angle it is pivoted or rotated. In one embodiment, the control slide 12 has an increasing displacement direction (i.e., first slide position) for increasing pump displacement and a displacement direction for decreasing pump displacement within the interior chamber of the housing. It can be displaced in the direction of decreasing the amount (that is, the second slide position). In one embodiment, the first slide position is the home position that can provide the maximum displacement by the pump, i.e. the position that increases the eccentricity between the control slide 12 and the rotor shaft as represented in FIG. Or defined as a direction. As the amount of eccentricity increases, the displacement or flow rate of the pump increases. Conversely, as the eccentricity decreases and the control slide 12 pivots from the first position to the second/reduced displacement position, the flow or displacement of the pump also decreases. Therefore, unlike the first slide position, the second slide position is defined as a position away from the first slide position (or a position away from the maximum discharge amount position), and as shown in FIG. Defined as the discharge rate position. Specifically, in one embodiment, the second slide position can include any number of positions remote from the first slide position, and in one embodiment, the slide is near the position of minimum output. , or it may be the position of the minimum discharge amount. In some embodiments, there may be positions with zero eccentricity. This means that the rotor and ring are coaxial. In this position, the high pressure side and the low pressure side have the same relative volume, so the flow rate is zero or very close to zero. Again, the function of this vane pump is known, and detailed description is omitted.

In embodiments where the control slide 12 pivots, the control slide 12 is pivotable or rotationally displaceable between slide positions about the pivot pin 28 within the interior chamber of the housing 20 as described above. A pivot pin 28 or similar pivoting or rotating feature may be provided for pivoting movement of the . A pivot pin 28 may be provided on the housing 20 . In one embodiment, the pivot pin 28 is mounted to the housing 20 within the internal chamber and the control slide 12 has a concave semi-circular bearing surface 34 that rides on the pivot pin 28, as shown. In some embodiments, the pivot pin 28 may extend through a hole in the control slide 12 rather than within an external carrying recess. The arrangement for pivotally connecting the control slide 12 to the housing 20 may have other arrangements, so these examples should not be considered limiting. In one embodiment, pivot pin 28 may be mounted within housing 20 adjacent outlet 40 . In one embodiment, pivot pin 28 may be provided within housing 20 on the opposite side of inlet 30 . In one embodiment, pivot pin 28 may be provided within housing 20 on a second radial side of rotor 15 . Further details regarding the placement of pivot pin 28 within housing 20 are provided throughout this disclosure.

The pump 10 also has a rotor receiving space 35 (or pocket). The rotor receiving space 35 may have a configuration and shape to complement the design, configuration or shape of the drive shaft 16 and rotor 15 and is configured to connect with the drive shaft 16 that drives the rotor 15 of the pump. may This rotor receiving space 35 communicates directly with the inlet and outlet and draws oil, lubricants or other fluids through inlet 30 under negative inlet pressure and out outlet 40 under positive outlet pressure. . In one embodiment, rotor receiving space 35 is defined by inner surface 13 of control slide 12 .

Rotor 15 is rotatably mounted within rotor receiving space 35 /inner surface 13 of control slide 12 within housing 20 . The rotor 15 rotates about an axis of rotation within and relative to the control slide 12 and is arranged to pressurize the fluid/lubricating oil injected from the inlet 30 via the inlet channel 39 . The central axis of rotor 15 is normally eccentrically positioned relative to the central axis of control slide 12 . The rotor 15 is connected to the drive input in a conventional manner, such as via a drive pulley, drive shaft, engine crank, or gear 11 (for use with the drive shaft), which is shown in FIG.

The rotor 15 has at least one radially extending vane 18 adapted for radial movement and a vane ring 19 . In the illustrated embodiment, multiple vanes 18 are shown. The at least one vane 18 is configured to engage an inner surface of the control slide 12 during rotation. Specifically, each of the vanes 18 is radially slidably mounted at its proximal end in a radial slot in the center ring of the rotor 15 . The centrifugal force forces the vane(s) 18 radially outwards and, during rotation, engages and/or engages the distal ends of the vanes with the inner surface 13 of the control slide 12. state is retained. This type of attachment is known in the prior art. Other variations may be used, such as using a resilient member, such as a spring, in the slot to bias the vanes radially outward. However, this example is not limiting. Thus, the vane(s) 18 are in sealing engagement with the inner surface 13 of the control slide 12 , for example by means of a vane ring 19 , so that when the rotor 15 rotates, a negative suction pressure is applied to the suction pressure. Fluid is drawn in through port 30 and discharged through outlet 40 with a positive discharge pressure. The control slide 12 can be moved (e.g., rotated) relative to the inner surface 13 of the slide 12 to change the position and movement of the rotor 15 and vanes 18, thereby adjusting pump displacement and outlet. The amount of lubricant dispensed from 40 can be varied.

The eccentric relationship between the control slide 12 and the rotor 15 creates a high pressure portion of the fluid on the side with the outlet 40 and a low pressure portion of the fluid on the side with the inlet 30 (in the art these are referred to as pumps). (referred to as the high pressure side and the low pressure side). As a result, fluid is sucked from the suction port 30 and discharged from the discharge port 40 . The function of this pump is known, and detailed description is omitted.

Typically, the resilient member 24 may urge the control slide 12 in the direction of increasing displacement, ie, toward the first slide position. In the illustrated embodiment, the resilient member 24 is a spring, such as a coil spring. According to one embodiment, the elastic member 24 biases the control slide 12 into the biased position and/or back into the initial position (i.e. in the direction of increasing delivery, e.g. at maximum eccentricity with the rotor 15). a first or home slide position), a biasing member. In one embodiment, the elastic member 24 may be provided on a first side of the control slide 12 and the pivot pin 28 is provided on a second side of the control slide opposite the elastic member 24 . may In one embodiment, the resilient member 24 may be provided on a first radial side of the rotor 15 and the pivot pin 28 may be provided on a second radial side of the rotor 15 (e.g. 2).

Housing 20 may include, for example, a receptacle 37 or notch for elastic member 24, partially shown in FIG. This receiving portion 37 is defined in part of the peripheral wall 23 to position and support an elastic member (spring), for example. Receptacle 37 may include a bearing surface against which one end of the spring engages. The control slide 12 includes a radially extending projection or bearing structure 58 that defines a bearing surface 59 with which the resilient member 24 engages, for example. Other structures or configurations may be used.

The control slide 12 may include a second radially extending projection 60 relatively opposite the first radially extending projection/structure 58, i.e. the projection 60 may be, for example, It may be on a second radial side of the rotor. Seals 62 and 64 may be attached to projections 58 and 60 (respectively), according to one embodiment. More specifically, in one embodiment, seals 62 and 64 may be provided between the inner surface of the interior chamber of housing 20 (ie, peripheral wall 23 ) and outer surface 17 of control slide 12 . In one embodiment, a first seal 62 may be provided adjacent resilient member 24 and a second seal 64 may be provided adjacent pivot pin 28 . In one embodiment, a first seal 62 is provided on a first radial side of rotor 15 and a second seal 64 is provided on a second radial side of rotor 15 . Seals 62 , 64 may define chambers 22 , 36 within the interior chamber of housing 20 , for example.

1-2 show a first (inlet) between housing 20 and control slide 12 for receiving pressurized lubricating oil within pump 10 (e.g., from a pressurized source such as a discharge line). Chamber 22 and second control chamber 36 between housing 20 and control slide 12 are shown. As seen in FIG. 1, for example, a circumferential portion of control chamber 36 is provided in the housing to extend to one side of slide 12, while a circumferential portion of chamber 22 extends to the other side of slide 12. side, the opposite/second side of the housing. The chamber 22 is connected to and forms part of an intake path 39 . First chamber 22 and second control chamber 36 each have at least one port for receiving pressurized fluid. For example, at least one port associated with control chamber 36 may communicate with outlet 40 of housing 20 for receiving pressurized fluid under positive outlet pressure. This pressurized fluid may also be received from other sources of positive pressure, such as an engine oil passage, a piston ejector, or the like. Also, bypassing the discharge pressure is not intended to be limiting.

First chamber 22 is controlled via second control chamber 36 and control slide 12 , ie, based on the position of control slide 12 and the amount of pressurized fluid supplied to control chamber 36 . As shown in FIG. 1, when the pressurized fluid supplied to the control chamber 36 is restricted, the first chamber 22, together with the resilient member 24, moves or urges the control slide 12 in its increasing direction. be able to. Based on the pressure of the lubricating oil supplied from the suction port 30 through the suction port 31, the slide 12 may be moved in the direction of increasing the discharge amount.

The second control chamber 36 is controlled in a conventional manner using passive control, for example, it may be controlled by outlet pressure or flow path pressure controlled by pressure feedback. That is, the force of positive pressure from the pressurized lubricating oil is applied to the second control chamber 36, which force is further applied to the control slide 12, causing the control slide 12 to eccentrically as shown in FIG. moves in the discharge amount decreasing direction (that is, the second slide position). For this reason, the second control chamber 36 is sometimes referred to as a pressure regulation or feedback control chamber 36 that is constructed and arranged to receive pressurized fluid to move the control slide 12 in a decreasing direction. In one embodiment, pressure changes within the control chamber 36 cause the control slide 12 to move or pivot (e.g., center) relative to the rotor 15 to adjust (reduce or increase) displacement within the pump. Sometimes.

At least the first seal 62 may define a pressure regulating chamber or control chamber 36 for receiving pressurized fluid. According to one embodiment, the feedback control chamber 36 is the chamber between the outer shape/surface 17 of the slide 12 and the inner chamber of the pump housing 20 and is positioned in the clockwise direction of the slide 12 with the pivot pin 28 and the first defined as a chamber extending between the seal 62 . As shown, feedback control chamber 36 extends to both first and second radial sides of rotor 15 . A second seal 64 may be provided on the side of the control slide opposite the feedback control chamber 36 . First chamber 22 may be defined in a clockwise direction between first seal 62 and second seal 64 . Also, the first chamber 22 extends to both the first and second radial sides of the rotor 15 .

The shape of the projections 58, 60 of the control slide 12 is not intended to be limiting. In one embodiment, one or both of these protrusions may include two converging surfaces (see, eg, protrusion 60 shown in FIG. 1). In one embodiment, one or both of these protrusions may include two parallel bearing surfaces (see, eg, protrusion 58 shown in FIG. 1). These projections 58, 60 may have any other structure or configuration. In the illustrated embodiment, projections 58, 60 each include a notch for receiving seals 62, 64 and corresponding structure therein. The seals 62 , 64 are positioned at the outer ends of the cutouts so that the seals 62 , 64 slide along the inner wall surface of the housing 20 as the control slide 12 moves or pivots within the housing 20 . may be placed in contact with the inner wall. In an alternative embodiment, the peripheral wall 23 of the housing may have a recessed area where the structure carrying the seals 62, 64 may be located. These recessed areas may be configured to allow the seals 62, 64 to maintain contact with the rings over the full range of movement of the control slide 12 based on movement of the rings, ensuring a tight seal. The specific shape shown is not intended to be limiting and may vary depending on the specific location of the seal, the travel allowed for the ring, the overall packaging of the pump 10, and the like. In one embodiment, any number of seals may be provided, for example between housing 20/cover 21 and control slide 12 . In the illustrated embodiment, the seal 62 is approximately 170° from the pivot pin 28, but this can be larger or smaller depending on various factors. These factors include (but are not limited to) limitations due to packaging method, desired pressure range, and the like. For example, seal 62 may be positioned anywhere between about 50° and about 180° (both ends included). The location of seal 62 is determined by the area required to generate a force against spring/elastic member 24 at the desired adjusted pressure, according to the embodiment. Seal 64 is positioned as close as possible to pivot pin 28 and to provide sufficient cross-sectional area for lubricant/oil to pass over and under slide 12 to channel 49 according to the embodiment. However, they are not overly restrictive. In the illustrated embodiment, seal 64 is provided adjacent discharge passage 49 to, for example, stop the flow of lubricating oil between discharge passage 49 and chamber 22 and/or intake passage 39 . there is

As shown in FIGS. 1 and 2, for example, the discharge channel 49 may have a first side and a second side, and the pivot pin 28 is located on the first side of the discharge channel 49. Or it may be provided within the housing 20 adjacent thereto, and the second seal 64 may be provided within the housing 20 on or adjacent to the second side of the discharge passage 49 . The interior of the control slide 12 may be formed with an outflow passageway 41 having first and second side edges aligned with the sides of the outflow channel 49 . Thus, in one embodiment, the pivot pin 28 may be provided within the control slide 12 (e.g., against the bearing surface 34) on the first side of the outflow passage 41, and the second seal 64 may It may be arranged in a notch in the slide 12 adjacent the second side of the outflow passage 41 . The outflow passage 41 is formed to allow the flow of lubricating oil under the slide 12 and through the passage 41 and thus between the top of the control slide 12 and the slide-facing side of the inner side of the cover 21 . (eg, molded). According to one embodiment, the depth of the outflow passage 41 (relative to the top surface of the control slide 12) may be about 3 mm to 4 mm (both ends included). This depth is limited by the amount of contact area required between the rotating vanes 18 and the inner surface 13 of the slide 12 .

Control slide 12 may further include a fluid receiving surface 43 therein for receiving and filling pressurized fluid from a portion of control chamber 36 . In one embodiment, the fluid receiving surface 43 is located on a first radial side of the rotor 15, for example near the spring or resilient member 24, adjacent to the first radially extending projection 58 of the control slide 12. may be provided. This bearing surface allows lubricant/oil to pass around the sliding contact with housing 20 when slide 12 is in its most eccentric position. Filling this fluid receiving surface 43 saturates the feedback channel 38 , which is connected to the main control valve 70 for controlling the pump 70 , with fluid, as further described below.

According to one embodiment, the position of the control slide 12 within the pump 10 is controlled by a main control valve 70 (represented schematically in FIG. 10), which controls the control behind the slide 12 . It is constructed and arranged to control the pressure in the chamber 36 and consequently affect the position of the slide and the displacement of the pump. The main control valve is sometimes called an "electrically operated valve". Although the term "motorized valve" is used throughout this disclosure, the term "motorized valve" is used herein to mean a regulating valve that is driven and controlled by an electrical signal, such as an electrical current. Obviously, the "motorized valve" in this disclosure may also be an electromechanical valve. In one embodiment, valve 70 is an electromagnetic valve that switches states using an external controller, such as a pulse width modulated (PWM) valve. In another embodiment, valve 70 is a variable current valve. In yet another embodiment, valve 70 is a solenoid valve. As such, there is no limitation as to the type of motorized or control valve 70 that may be used with pump 10 . In general, the use of such main control valves or electrical (PWM) valves 70 in pumps is generally known in the art, and thus, except for a few additional features described below, their function will be apparent to those skilled in the art. commonly understood by

Motorized valve 70 is connected to control port 42 provided in housing 20 . FIG. 3 is a side view of housing 20 showing an exemplary location of control port 42, i.e., adjacent intake port 30. FIG. Port 42 is an input control port (eg, from the engine block and/or from PWM/main control valve 70 ) and is in fluid communication with port or passage 45 . Ports 42 may be drilled, formed, or machined into the housing. Passage 45 is a passageway or channel drilled, formed or machined into the pump housing. Holes or ports 42, 45 are added/designated for communication with the feedback channel. Specifically, as shown, connected to control port 42 via drilled passage 45 is feedback channel 38 (i.e., control port 42 is a hole/passage 45 to the feedback channel). A feedback channel 38 is formed in the housing 20 to provide a path for fluid/lubricant flow from the electrically operated valve 70 to the feedback control chamber 36 . By fluidly connecting the motorized valve 70 to the control chamber 36 and the feedback channel 38 via the control ports 42 (and 45), the pressure (and the amount of lubricating oil) within the control chamber 36 can be controlled. can.

Feedback channel 38 is sometimes referred to as a vent channel for evacuating fluid. In some cases, evacuation is based on the position of motorized valve 70 . In one embodiment, when the control slide 12 needs to increase the displacement, the control valve is through the feedback channel 38, the passage 45, and the control port 42, through the motorized valve (or another control valve). It is configured to drain [fluid/lubricant] from the control chamber 36 so that the fluid/lubricant returns to the lube sump (eg, lube sump 14 or tank).

Feedback channel 38 and ports 42/45 remain open to electrically controlled (PWM) valve 70 under all conditions and conditions, including during cold start. However, flow through channel 38 may be restricted based on pump conditions. During normal operation and use of pump 10 , for example, feedback channel 38 receives sufficient (warm) lube/oil/fluid from main control valve 70 . In this case, for example, "sufficient" means normal flow of lubricating oil through channel 38 . During a cold start, for example, the size and dimensions of the system feedback channel to the main control valve 70 and the system feedback channel from the control valve to the port 42 limit or limit the movement of cold lubricating oil therethrough. , delaying the pressure response to the feedback channel 38 and thus the control chamber 36 . This causes pressure to build up in outlet channel 49 and move upstream in the system. As will be described in more detail below with reference to the high pressure relief valve 44, pressure build-up in the discharge port will allow the flow of fluid into the control chamber 36, including control of the control slide 12, even when the lubricating oil is cold. affect feedback.

According to one embodiment, the feedback channel 38 is designed to be narrow enough to restrict the flow of cold lubricant therein for a period of time, but to allow cold lubricant to flow during a cold start. there is This restriction allows pressure to build up quickly within chamber 36 when relief valve 44 is actuated (also described in detail below). However, feedback channel 38 is unrestricted at the regulated flow level from control valve 70 . Lubricant communication to/from control chamber 36 via feedback channel 38 may be enabled not only during normal operation of the pump, but also during fail-safe conditions.

In one embodiment, feedback channel 38 is added to the pump housing. That is, the vent channel may be added (eg, machined) into an existing pump housing. Arrangement of the feedback channel 38 is not particularly limited. In one embodiment, feedback channel 38 is positioned adjacent elastic member 24 . In one embodiment, feedback channel 38 is positioned adjacent first seal 62 . In one embodiment, feedback channel 38 is positioned adjacent to inlet 30 . In another embodiment, the feedback channel is provided on the first radial side of rotor 15 . In yet another embodiment, a feedback channel is provided between the housing and the cover. In yet another embodiment, the feedback channel is formed in a wall defining the interior chamber of the housing. Such embodiments are not intended to be limiting. In practice, a combination of these embodiments may be implemented in pump 10 . For example, as shown in FIG. 2, according to one embodiment, the feedback channel 38 is on a first radial side of the rotor 15 adjacent the resilient member 24, the first seal 62, and the inlet 30. , may be designed to be placed between the housing 20 and the cover. Additionally, the illustrated embodiment is not intended to limit the location of feedback channel 38 . In some embodiments, for example, feedback channel 38 may be connected to a central portion of control chamber 36 (eg, along line RR) and/or adjacent pivot pin 28, for example. may be provided as Although located within housing 20 , feedback channel 38 is designed to be pressurized and vented via motorized valve 70 .

Pump 10 may also include a high pressure relief valve 44 (eg, controlled by outlet pressure in passage 49) provided in housing 20, with electrical (PWM) valve 70 connected thereto. As previously mentioned, the disclosed relief valve 44 may be, for example, a spool valve. Valves 44 and 70 are separate and not fluidly connected. However, relief valve 44 can also provide feedback and control of pump 10 . For example, the relief valve 44 may reduce eccentricity by providing pressure relief when the pressure in the outlet is too high, thereby reducing the flow rate in the pump.

1 and 2 are diagrams showing an example of the position of the relief valve 44 (and its housing) within the housing 20. FIG. In one embodiment, relief valve 44 (and its housing) is positioned within housing 20 on a second radial side of rotor 15 . In one embodiment, the relief valve 44 is located near or adjacent to the pivot pin 28 of the control slide 12 of the pump 10 . In one embodiment, pressure control relief valve 44 is positioned within housing 20 below pivot pin 28 . Relief valve 44 is generally designed to be connected to the outlet space via outlet path 49 and to feedback control chamber 36 of pump 10 . Thus, as shown in FIG. 3 and as seen in the cross-sectional view of FIG. 4, a relief valve 44 may be positioned adjacent discharge port 33 within housing 20, according to an embodiment.

FIG. 5 is an alternative cross-sectional view of relief valve 44 showing an example of further detail of relief valve 44 . According to one embodiment, relief valve 44 has a spool body 46 having a working surface 68 in fluid communication with discharge passage 49 . In one embodiment, working surface 68 may be the front surface of body 46 . Generally, the relief valve 44 will be positioned in the first valve position (or FIG. 7) to a second valve position (ie, a position away from the first valve position shown in FIGS. 8-9).

According to one embodiment, the pressure control relief valve 44 includes a spring 48 for biasing the body 46 to the first valve position. The spring 48 may be provided within a receiving opening 47 of the body 46, as shown in FIG. Spring 48 exerts a spring force on body 46 to move body 46 to a first valve position, i.e., toward wall abutment 66 (see also FIG. 6), to a closed or unactuated position (further details below). described). In one embodiment, the disclosed pressure control valve 44 fits within a machined valve space 50 . That is, in one embodiment, valve space 50 (or valve housing) is molded, formed, drilled, or machined into pump housing 20 such that valve space 50 is integrally formed as part of the pump. may Accordingly, valve 44 components (eg, valve body 46 and spring 48) may be located in designated areas of the pump housing. In one embodiment, a pin 54 may be provided within the valve space 50 to securely hold the ends of the body 46 and spring 48 within the housing and space 50 . In the illustrated embodiment, for example, the pin 54 is positioned perpendicular to the longitudinal direction of the body 46 at one end of the body 46 while the other end, ie, the actuation surface 68 is in fluid communication with the discharge channel 49 . is provided. In another embodiment, a housing designed to house the components of valve 44 may be inserted into a designated area of pump 10 (eg, space 50).

In addition to providing a valve space 50 or housing for the relief valve 44 within the housing 20, a supply control space 52 is provided. A supply control space 52 connects at least a portion of the discharge path 49 (e.g., a portion of the discharge port 33) to the valve space 50 of the pressure control relief valve 44 and channels output pressurized lubricating oil therein. configured to accept As will be described in detail below, lubricating oil pressure is configured to build up within the supply control space 52 such that when a predetermined output pressure or threshold is reached and/or exceeded, the relief valve 44 will It is adapted to move away from the first valve position and into the second valve position. More specifically, the supply of lubricating oil from discharge passage 49 through supply control space 52 results in the build-up of pressure on working surface 68 of body 46 , resulting in pressure control relief valve 44 pressure. A force may be applied to the actuation surface 68 to move the body 46 and compress the spring 48 . The aforementioned wall abutment 66 limits movement of the body 46 into the housing 20 and into the supply control space 52 when the pressure in the supply control space is below or below the predetermined output pressure.

Housing 20 also includes, for example, relief port 56 shown in FIGS. Relief port 56 selectively communicates fluid from discharge path 49 (eg, from discharge port 33 ) to feedback control chamber 36 based on the position of pressure control relief valve 44 . In one embodiment, relief port 56 is positioned between and communicates with valve space 50 and feedback control chamber 36 . In some embodiments, relief port 44 may be provided below control slide 12 within housing 20 .

Relief valve 44 is actuated to move toward or to the second valve position to control the pressure on feedback control chamber 36 during any state or setting of motorized valve 70. may be made That is, the main control/motorized valve 70 is configured to control the pressure in the control chamber 36 independently of the position of the relief valve 44, and this control involves moving the control slide 12 in the direction of decreasing discharge. This includes delivering pressurized lubricant to pressurize the control chamber 36 for displacement and expelling the pressurized lubricant from the control chamber to allow for increased displacement of the control slide. . This is because the electric valve 70 and the relief valve 44 are not fluidly connected. Relief valve 44 is controlled via pressure build-up in outlet space 52 and outlet passage 49 while motorized valve 70 is switched between supply and outlet states using an external controller. The relief valve 44 does not block any control of the pump 10 from the motorized valve 70 . Rather, the relief valve 44 simply acts as a relief or failsafe when the pressure within the outlet space exceeds a predetermined value or threshold.

In operation, in its first valve position (or closed or initial position) as shown in FIGS. to block fluid communication to the control chamber 36 . Spool body 46 is biased by spring 48 (toward the right as shown in FIG. 6) such that front/working surface 68 thereof contacts wall abutment 66, and body 46 is in relief. Blocks port 56 , thus restricting any flow from supply control space 52 to relief port 56 . Therefore, the feedback function is disabled. Fluid communication is provided through outlet path 49 to outlet 40 during normal operation of the pump. Independently of this, the main control valve 70 operates in this normal operation to control the pressure in the pump, and thus the position of the slide 12 and/or pressurize the control chamber 36. may be used inside.

When pressure is applied within the supply control space 52, the pressurized lubricating oil is forced against the working surface 68 of the body 46, as indicated by the arrows in FIG. When the outlet pressure of the lubricating oil in the supply control space 52 exceeds a predetermined amount or threshold, the outlet pressure acts on the actuating surface 68 of the relief valve 44 and acts on the second valve as shown in FIGS. Actuation surface 68 may be moved toward the position (or open or actuation position) and/or to the second valve position. In this second valve position, as shown in FIG. 8, body 46 and at least a portion of front/actuating surface 68 have moved beyond relief port 56 (toward the left as shown in FIG. 8). Alternatively, at least a portion of the relief port 56 may be open to allow fluid flow from the supply control space 52 through the relief port 56 to the control chamber 36 . Thus, in the second valve position, the relief valve 44 permits fluid communication of lubricant from the discharge passage through the relief port 56 to the control chamber 36, thereby pressurizing the control chamber 36 and causing the main control valve to It is possible to displace the control slide 12 in the direction of reducing the delivery rate independently of. That is, the relief valve is actuated by allowing fluid flow from the discharge path to the control chamber 36 . The addition of lubricant to the feedback control chamber 36 in turn reduces the amount of eccentricity of the control slide 12 .

As the discharge rate decreases, the pressure in the discharge path and supply control space 52 also decreases. Accordingly, spring 48 may be configured to return body 46 of valve 44 to its first valve position, blocking relief port 56 .

The predetermined amount or threshold amount of pressure required to actuate the relief valve 44 may be based on customer requirements, for example. In one embodiment, the pressure to open the valve (ie the pressure to actuate the pressure control relief valve 44 to hydraulically move it to the second position) is about 6 bar. For example, when the pressure directed into the valve body 46 via the supply control space is less than 6 bar (or any predetermined pressure amount or threshold amount), the valve 44 as shown in FIGS. remains in the first valve position. However, once the pressure is above about 6 bar (or a predetermined pressure, threshold pressure or selected pressure), the valve 44 may be hydraulically/mechanically moved to its second valve position, which This allows, for example, lubricating oil to flow through relief port 56 .

The dimensions of relief valve 44 and its components are not intended to be limiting. In one embodiment, the body 46 of the relief valve 44 has a width W2 that is less than the width W of the valve space 50 such that the body 46 moves relative to and within the space 50. obtain. Additionally, the width W4 of the feed control space 52 may be less than the body width W2 such that the wall abutment 66 contacts at least the edge of the front/working surface 68 of the body 46 . The width of the spring 48 and/or its coils is less than the width W3 of the receiving opening 47 according to one embodiment.

Further, the pump 10 according to one embodiment may be provided with a ball valve as shown in FIGS. 1 and 2 . The cover 21 may be designed with channels/openings for connecting the discharge passage 49 to this ball valve. Generally, the use of ball valves of this kind is well known in such pumps. In some cases, ball valves may not be able to handle discharge pressures (e.g., 6.5 bar and above). However, in the disclosed configuration, if the high pressure relief valve 44 were to become stuck or disabled, the pump assembly 10 would still use this ball valve as a backup pressure actuated ball relief valve to relieve pressure in the outlet passage 49. have.

Accordingly, the disclosed pressure control relief valve 44 is a proportional control valve that controls pressure within the control chamber 36 without the use of the motorized valve 70 . The relief valve 44 is a separate and distinct relief function and does not depend on the PWM control supply to/from the control chamber. The relief valve 44 is a hydraulically actuated valve that provides a mechanically designed method of moving the spool valve such that the pressure build-up in the discharge space is used to supply lubricant/fluid to the feedback chamber of the pump. be. Relief valve 44 provides a fail-safe function that operates on pressure alone (ie, does not use a separate control valve). Further, the design and location of this relief valve 44 does not occlude any channel returning to the vent/feedback channel 38 or the motorized valve 70, except for the relief port 56 to the control chamber itself. However, the feedback channel 38 to the motorized valve 70 is always open and is designed with a restrictive cross-section.

Relief valve 44 provides protection from high pressure during initial startup of pump 10 (i.e., during pump or system cold starts and/or during other operations where the fluid (or lubricant or oil) is colder). can be provided. The feedback channel 38 is configured to be less restricted than the channel through the control valve 70 so that that valve can maintain authority over the control slide 12 when the system is in normal operating mode. However, the system/pump will generally operate when the control valve 70 adjusts the control slide 12, e.g., when the [oil] passage fills with fluid/lubricant/oil when the engine is first started, and when the fluid A time delay occurs when the /lubricant/oil is too cold to flow enough to displace the control slide 12 sufficiently. Such a time delay causes pressure to build up in the outlet passage, thereby opening the relief valve 44 (i.e., the built-up pressure causes the relief valve 44 to open from the closed or initial first valve position). state to the second valve position). This means that with cold oil/lubricant (e.g. when cold starting the pump), pressure builds up slowly in the control chamber 36 (because the cold, viscous lubricant moves more slowly). . When the lubricating oil is cold, movement through the passageways including feedback channel 38 and ports 42, 45 is restricted but allowed for a period of time. Fluid/lubricant/oil from the relief valve is supplied directly to control chamber 36 and can flow through channel 38 towards control valve 70 . After a while, the outlet pressure also rises. However, the higher flow rate of fluid/lubricant/oil from valve 44 passes through the more restrictive feedback channel 38, ports 45, 42 and attempts to return through valve 70, resulting in a pressure loss (or pressure differential). ), acting on the control slide 12, it can be displaced to a lower displacement (ie in the direction of decreasing delivery). This displacement of the slide 12 lowers the outlet pressure and closes the relief valve 44 . In some embodiments, pressure on the outlet, and thus the supply control space 52, moves the spool body 46, opening the relief port 56 and feeding back into the control chamber 36, allowing the lubricating oil to cool and cool. The slide 12 may be controlled for some time. Once the delay time has passed and the pressure reaches the control valve, normal control operation of the pump 10 is initiated.

The present disclosure also provides pump 10 with features including main control valve 70, feedback channel 38 and relief valve 44, and by providing control mechanisms for controlling pump 10 and its features. It should be understood that it covers methods of reducing the amount of eccentricity of a variable vane pump such as the pump 10 described therein. The method comprises hydraulically moving the pressure control relief valve 44 from a first valve position to a second valve position based on a predetermined pressure of the lubricating oil acting on the working surface and relieving the lubricating oil from the discharge path. and pressurizing the control chamber 36 by fluidly communicating with the control chamber 36 through the port to displace the control slide 12 in a decreasing flow direction independently of the main control valve 70 . The main control valve 70 is configured to control the pressure in the control chamber 36 independently of the position of the relief valve 44, and includes controlling the control slide 12 to displace the control slide 12 in a decreasing direction. This includes delivering pressurized lubricant to pressurize the control chamber 36 and expelling the pressurized lubricant from the control chamber to permit displacement of the control slide 12 in an increasing displacement direction.

Although the drawings and description refer to the use of a main control valve and a pressure control relief valve in a vane pump, the valve system disclosed herein can also be used in different pump applications.

FIG. 10 is a schematic diagram of system 25 according to one embodiment of the present disclosure. System 25 is, for example, a vehicle or part of a vehicle. System 25 includes a mechanical system such as an engine 32 (eg, an internal combustion engine) that receives pressurized lubricant from pump 10 and lubricant sump or tank 14 . Pump 10 receives lubricant (eg, oil) from lubricant source 26 (via inlet 30 ), pressurizes it, and supplies it to engine 32 (via outlet 40 ). Pump 10 includes at least a main control valve 70 operatively connected thereto and a pressure control relief valve 44 housed in housing 20 thereof. As detailed above, the pressure control relief valve 44 in the pump 10 selectively moves to its second valve position when the outlet pressure is above a predetermined/threshold level to discharge lubricant. It is configured to return from the path/discharge port to the control chamber 36 via the relief port 56 .

While the principles of the present disclosure have been made clear in the above exemplary embodiments, various changes can be made in the structure, arrangement, proportions, elements, materials and components used in practicing the present disclosure. It can be understood by those skilled in the art.

Thus, even with such variations, the features of the present disclosure will be fully and effectively achieved. The preferred specific embodiments above have been described and illustrated for purposes of illustrating the functional and structural principles of this disclosure, and may be varied within the scope of such principles. Accordingly, this disclosure includes all modifications that fall within the spirit and scope of the appended claims.

Control slide 12 may further include a fluid receiving surface 43 therein for receiving and filling pressurized fluid from a portion of control chamber 36 . In one embodiment, the fluid receiving surface 43 is located on a first radial side of the rotor 15, for example near the spring or resilient member 24, adjacent to the first radially extending projection 58 of the control slide 12. may be provided. This bearing surface allows lubricant/oil to pass around the sliding contact with housing 20 when slide 12 is in its most eccentric position. This filling of the fluid receiving surface 43 saturates the feedback channel 38 , which is connected to the main control valve 70 for controlling the pump 10 , with fluid, as further described below.

Housing 20 also includes, for example, relief port 56 shown in FIGS. Relief port 56 selectively communicates fluid from discharge path 49 (eg, from discharge port 33 ) to feedback control chamber 36 based on the position of pressure control relief valve 44 . In one embodiment, relief port 56 is positioned between and communicates with valve space 50 and feedback control chamber 36 . In some embodiments, relief port 56 may be provided below control slide 12 within housing 20 .

Claims (16)

A variable displacement vane pump for discharging lubricating oil into a system,
a housing having an interior surface defining an interior chamber;
a suction port for injecting and pressurizing the lubricating oil into the housing, the suction port being connected to a suction path in the housing;
a discharge port for delivering pressurized lubricating oil from the housing to the system, the discharge port being connected to a discharge passage provided in the housing;
A control slide displaceable within the interior chamber of the housing about a pivot pin, the control slide having (a) an increasing displacement direction to increase pump displacement and (b) a decreasing pump displacement. a control slide displaceable in a direction of decreasing displacement, said control slide having an inner surface defining a rotor receiving space;
A rotor having at least one vane mounted in the rotor receiving space of the control slide, the rotor rotating within the control slide relative to the control slide about an axis of rotation to provide the suction a rotor configured to pressurize the lubricating oil injected via a passage, the at least one vane being configured to engage the inner surface of the control slide during rotation;
The suction port and the discharge port are disposed on opposite radial sides of the rotation axis of the rotor, the suction port is provided on the first radial side, and the discharge port is on the first radial direction. provided on a second radial side opposite the side,
A resilient member biasing the control slide in the direction of increasing discharge, the resilient member being provided on the first radial side of the rotor, and the pivot pin being located on the second radial side of the rotor. an elastic member provided on the side;
a control chamber for receiving pressurized fluid provided between said housing and said control slide, said pressurized fluid being constructed and arranged to move said control slide in said decreasing direction; a control chamber, said control chamber extending to both said first radial side and said second radial side of said rotor;
a relief port in the housing for selectively communicating fluid from the discharge passage to the control chamber;
a feedback channel within the housing and fluidly connected to a control port, the control port being connected to a main control valve configured to control pressure within the control chamber; When,
A pressure control relief valve within the housing, the relief valve having an actuating surface in fluid communication with the discharge passage and having a predetermined amount of the lubricating oil acting on the actuating surface. a pressure control relief valve movable from a first valve position to a second valve position based on the pressure of
The main control valve is configured to control the pressure in the control chamber independently of the position of the relief valve, the control for displacing the control slide in the direction of decreasing delivery. delivering pressurized lubricant to pressurize said control chamber; and expelling pressurized lubricant from said control chamber to enable displacement of said control slide in said increasing displacement direction;
in the first valve position, the relief valve is inactive and blocks fluid communication from the discharge passage through the relief port to the control chamber;
In the second valve position, the relief valve permits fluid communication of the lubricant from the discharge passage through the relief port to the control chamber, thereby pressurizing the control chamber and controlling the main control. displacing the control slide in the direction of decreasing the discharge rate independently of the valve;
Variable displacement vane pump. When the relief valve is in the second valve position, the feedback channel restricts fluid flow through the feedback channel for a period of time, thereby causing pressure to build up in the control chamber and creating a pressure differential. 2. The pump of claim 1, configured to displace the control slide in the direction of decreasing displacement. 2. The pump of claim 1, wherein the pressure control relief valve is positioned within the housing on the second radial side of the rotor. 2. The pump of claim 1, wherein the suction passage is provided adjacent to the resilient member and the discharge passage is provided adjacent to the pivot pin. 2. The pump of claim 1, wherein the pressure control relief valve is positioned within the housing adjacent the pivot pin. Further comprising a supply control space within the housing, the supply control space connecting the discharge path to the pressure control relief valve and configured to receive output pressurized lubricant, the pressure of the lubricant being above the configured to accumulate within a supply control space, wherein upon reaching and/or exceeding said predetermined output pressure, said relief valve is moved to said second valve position; 1. The pump according to 1. The pressure control relief valve comprises a body and a spring, and in the second valve position the lubricating oil from the discharge passage is supplied through the supply control space to move the body of the pressure control relief valve. 7. A pump according to claim 6, configured such that application of a force results in compression of the spring by movement of the body. 2. The pump of claim 1, wherein said relief port is provided within said housing below said control slide. 2. The pump of claim 1, wherein said feedback channel is positioned adjacent said resilient member. 2. The pump of claim 1, wherein the feedback channel is positioned adjacent to the inlet. 2. The pump of claim 1, wherein said feedback channel is provided between said housing and cover. 12. The pump of claim 11, wherein said feedback channel is formed in a wall defining said internal chamber of said housing. 2. The pump of claim 1, wherein said system is an engine. engine and
a lubricating oil sump containing lubricating oil;
and the variable displacement vane pump of claim 1 for delivering said lubricating oil to said engine. A method for reducing the eccentricity of a variable vane pump comprising the pump of claim 1, comprising:
hydraulically moving the pressure control relief valve from the first valve position to the second valve position based on the predetermined pressure of the lubricating oil acting on the working surface;
permitting fluid communication of the lubricating oil from the discharge passage through the relief port to the control chamber, thereby pressurizing the control chamber to move the control slide to the discharge rate independently of the main control valve; and displacing in a decreasing direction,
The main control valve is configured to control the pressure in the control chamber independently of the position of the relief valve, the control for displacing the control slide in the direction of decreasing delivery. delivering pressurized lubricant to pressurize the control chamber; and expelling pressurized lubricant from the control chamber to permit displacement of the control slide in the direction of increasing displacement;
Method. while permitting fluid communication of the lubricant from the discharge passage through the relief port to the control chamber when the relief valve is in the second valve position;
When the lubricating oil is cold, the feedback channel restricts fluid flow through the feedback channel for a period of time, thereby causing pressure to build up in the control chamber and creating a pressure differential to move the control slide to the 16. The method of claim 15, configured to displace in a direction of decreasing output.

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